Lubricant pump



May 3l, i960 T. R. THOMAS LUBRICANT PUMP '7 Sheets-Sheet 1 Original Filed Feb. 13, 1951 w M llm Rm my @N WR. m m Y Y @w A @2 n mm Si NNN NNN a m @mug NN AAN Qhmmwm N N www m w3 RSN m om. E@ 1% www wm o NQ m, \\m. NNN WNW?) OWN/Q N www m www@ K O /W Q MQ $1 N U www Q Ew 3, ,mwN U o .1 www @Q www W S1 Q2 Tw G www QN mw @n mm. .w N mwN www. N ,A www@ www1 Rm Q @WWW @www U C f um Sw v N w m m H w \N\\/ Wm w A um uN s J @w mw mw ma mm. Mw mw @S1 @S1 m T. R. THOMAS LUBRICANT PUMP original Filed Feb. 1s. 1951 7 Sheets-Sheet 2 INVENTOR j Twfw Zwama mk u 1 May 31, 1960 T. R. THOMAS 2,938,500

LUBRICANT PUMP Original Filed Feb. 13, 1951 7 Sheets-Sheet 3 NM M M www w. am

@N www @WN Q mRM m www www m L? l s T. R. THOMAS LUBRICANT PUMP May 31, 1960 7 Sheets-Sheet 4 Original Filed Feb. 13 1951 www@ QNN NNN www# INVENTOR Malla/0S JE Mms T. R. THOMAS LUBRICANT PUMP May 31, 1960 7 Sheets-Sheet 5 Original Filed Feb. 13

ATTORNEYS T. R. THOMAS LUBRICANT PUMP May 31, 1960 7 Sheets-Sheet 6 O riginal Filed Feb. 13, 1951 bww INVENTOR flaws/ms' j? Timm/a ATTORNEYS mww bmw www www mwmh @MEI bmw ANN NNN Original Filed Feb. 13, 1951 7 Sheets-Sheet 7 @05 653 i? 262 @e2 Q7! 272 6x8 621 625 @f5 @fg 5;@ 624 629 0 @D @f6 l? 55 INVENTOR LUBRICANT PUlVIP Thomas R. lThomas, New York, N.Y., asslgnor to Auto Research Corporation, Dover, Del., a corporation of Delaware Original application Feb. 13, 1951, Ser. No. 210,725,

now Patent No. 2,710,670, dated June 14, 1955. Divided and this application .lune 14, 1955, Ser. No. 515,476

1 Claim. (Cl. 1S4-27) This invention relates to' a lubricating system and it particularly relates to a centralized lubricating system.

This application is a division of application Serial No. 210,726, tiled February 13, 1951, now Patent No. 2,710,670.

Although not limited thereto, the present invention will be particularly described in its application to a centralized lubricating installation of the high restricting ow metering type in which a plurality of widely distributed and spaced bearings-are to receive relatively small, yet accurately proportioned quantities of lubricant during the operation of the mechanism being lubricated, which quantities will give sufficient and ample lubrication without overow or excess lubricant on the machine regardless of the relative inaccessibility and accessibility of the bearings, varying climatic conditions and various temperatures that may cause changes in the viscosity of the lubricant regardless of the amount of operation of the machine.

In the preferred form of the present invention there is provided a central pump automatically actuated by the machine or associated mechanism to feed lubricant in a cyclic manner in accordance with the length and period of operation of the machine.

From this pump there extends a branched distributing conduit or piping system to a plurality of widely distributed bearings in or about the mechanism to be lubricated, whether it be an automotive chassis, a'machine tool, a textile machine, a power press, a baking machine, an accounting machine, and many other types of mechanisms and machines.

At the outlets of the system and adjacent to or directly on the bearings or connected to the bearings by tail pipes are high restriction ow metering fittings which may have inlet strainers, outlet check valves, preferably spring seated, and intermediate high restriction members which, in the preferred form, consist of a pin closely fitting in a bore, both of accurately predetermined dimensions.

These high restriction ow metering fittings have an obstructing or restricting eiect upon the flow of lubricant which is tremendously greater than that afforded by the piping or tubing system, even though quite elongated to the most remote bearing and also tremendously greater than the obstructing or restricting effect encountered in the bearing.

It is among the particular objects of the present invention to provide an improved, reliable pump or pressure unit for a centralized lubricating installation of the high lubrication flow metering type which will give suicient and ample lubrication without overow or excess lubricant on the machine regardless of Varying climatic conditions and various temperatures that may cause changes in the viscosity of the lubricant in accordance with the requirements of the machine bearings.

Another object of the present invention is to provide a novel central pressure source for lubricating installations of the character described, in which said pressure source will supply lubricant under pressure to a lubricat- 2,938,60 Patented May 31, 19760 ing installation ofthe character described at predetermined intervals, in accordance with the length and amount of operation of the mechanism being lubricated.

Another object is to provide a compact, durable, reliable, central pump installation for a lubricating installation of the character describedwhich will be automatically actuated by the mechanism being lubricated to supply the proper portions of lubricant thereto throughout theoperaton of the machine.

Still further'objects and advantages will appear in the more detailed description set forth below, it being understood, however, that this more detailed description is given by way of illustration and explanation only and not by way of limitation, since various changes therein may be made by those skilled in the artwithout departing from the scope and spirit of the present invention. r

In accomplishing they above objects, it has been found most satisfactory, according to one embodimentof the present invention, to provide a central reservoir which may take the form of a separate casing or which'may take the form of a lubricant pocket in the machine bein lubricated.

v The pump and driving mechanism preferably is assembled as a single unit with the cover of the reservoir or pocket serving to carry the depending reciprocating piston pump as well as the actuating mechanism.

In the preferred form of the invention, suspended from the cover of the mechanism by a U-shaped bracket is a cylinder receiving a piston pump and carrying at its lower end an inverted filter cup. i

The upper part of the piston is preferably provided with a connection to a reciprocatory arm, which at determined intervals will lift the piston, drawing in a charge of lubricant and compressing a return spring.' lThe spring upon the release will return the piston andforce' 'said lubricant into the external branched system.

Desirably Van adjustment is provided to permit regulation of the stroke of the piston.

The pump is desirably actuated by a horizontal shaft mounted in a bearing on the cover of the pump from a reciprocating or rotating part of the mechanism being lubricated. The bearing for the shaft is Vdesirably lubricated from the pump and it carries a worm which in turn drivesz a gearing train. This train with a suitable reduction will drive a camA to cause elevation of .a lever acting upon the plunger. v

Desirablythe gearing train is positioned within the reservoir' so that it will be directly lubricated by the lubricant therein and the shafts for the gearing train are mounted in the brackets depending from the cover and extending downwardly inside the reservoir casing or pocket. y

With the foregoing and other objects in view, the invention consists Vof the'novel construction, combination and arrangement of parts as hereinafter more specifically described, and illustrated in the accompanying drawings, wherein is shown an embodiment of the invention, but it is to be understood that changes, variations and modications can be resorted to whichfall within the scope of the claim hereunto appended. v

In the drawings wherein like reference characters denote corresponding parts throughout the several views:

Fig. 1 is a side elevational view from the line 1--1 of Fig. 2 and partly in section, showing a pump unit assembly according to the preferred embodiment of the present invention.

Fig. 2 is a side elevational view partly in section the line 2--2 of Fig. 1.

Fig. 2a is a fragmentary side elevational view showing the lubrication feed to' the bearings on the cover.

Fig. 3 is a transverse horizontal sectional view taken upon the line 3-3 of Fig. 1.

upon

assenso Fig. 4 is a horizontal transverse sectional view taken. upon the line 4 4 of Fig. 1.

Fig. 5 is a fragmentary top view partly in section similar to Fig. 4, taken upon the. line 5--5 of Fig. 6. Y

Fig. 6 is a vertical transverse section view takenupon the line 6--6 of Fig. 5.

Y Fig. 7-` isa to'p plan view similar to Fig. .5 of an alternative drive. construction taken upon the line 7-7 of Fig. 8.

Fig. 8: is a side vertical sectional view taken upon the line 8-8 of Fig. 7.

Fig. 9 is a fragmentary vertical sectional view taken upon the line 9-9 of Fig. 7.

Fig. 10 is a top plan view partly in section of an alternative construction taken from the line 10-10 of Fig. 11.

Fig; 11 is a transverse vertical. sectional View taken upon the line 11-11 of Fig. 10.

Fig. 1.2 is a vertical sectional view ot'. an alternative construction.

Fig. 13 is a side elevational view of the structure of Fig. 12.

Fig. 14 is a diagrammatic side elevational view partly in section and upon a reduced scale as compared to Figs. 1 to 13, showing the pump as applied to a mechanism with an actuating cam.

Fig. 15 is a fragmentary top elevational view of a detail o'i the; drive mechanism.

Fig. 16' is a fragmentary side. perspectivev view showing f the pump ofthe present invention as applied to. a punch press.

Fig. 17 is a. longitudinal sectional view'of a preferred type of ow meter unit which may be used.

Fig. 17a is a longitudinal transverse sectional view of a type, of ow meter unit which may also be employed.

Fig. 18 is a fragmentary transverse sectional view of an alternative form o'f drive arrangement showing a drive ratchet and a detent ratchet.

Fig. 19 is a transverse vertical sectionalview of the detent ratchet upon the line 19-19 of Fig. 18.

Fig. 20 is a transverse vertical sectional view upon the line 20-20 of Fig. 18, showing the drive ratchet.

Fig. 21 is a side elevational view of one type of drive connection. r

Fig. 22 is a top plan view of said drive connection of Fig. 21. f

Fig. 23 is a side elevational view of an alternative type of drive connection similar to Fig. 21.

Fig. 24 is a top plan view of said drive connection of Fig. 23. Y v

Referring to Figs. l to 4, the cover or support member A is provided with a bracket B which carries the pump C. The pump C is driven by the connection D and the drive mechanism E on the cover to the depending drive mechanism F (see Pigs. l and 2).

The cover A has corners 20 (see Fig. 4) which receive screws or bolts 21 extending in the upper wall. 22 of the reservoir R. Extending upwardly from the cover A is the filler neck 23 provided with a clo'sure 24 having the hinge 25 and the breather openings 26.

The cover A has an integrally formed sleeve portion 27 in which is positioned the bearing sleeve 28 carrying the shaft 29 (see Fig. 4). The shaft 29 has the recessed por` tion 30 and the enlarged bearing portions 31 and 32. The sleeveV 28 has the lubricating groove 47 with radial bores 48.

The shaft also has a reduced diameter extension 33 which carries the ratchet 34. The ratchet 34 serves as a driver ratchet wheel. The driver ratchet wheel 34 is received in the cup 35 formed by the projecting sleeve 36. The sleeve 36 is a o'ne piece malleable Ycasting or drop forging. The cup 35 is closed by the cap 37 having the threaded nipple 38.

40 with the screw holes 41. whichr receive the bolts 42 holding the cover plate 43 in position thereo'n. The rings 44 and 45 on sleeve 28 bear against the plate 43. Extending downwardly from the sleeve 28 is the actuating lever (see Fig. 1).

The lever 55, which is shown in. section (in Fig. 2), has a tapped opening which receives the threaded plug 76 to hold spring 77 in place. The spring 77 is received in arecess 78 inthe ratchet pawl 79 which ts in the opening in the upper part of the lever 55. The stop pin 81 limits rotary movement of the pawl 79. i

At the innerend ofthe sleeve-28 isthe. washer: 54. Beyo'nd the washer 54 is the detent ratchet 56 tted upon the reduced diameter shaft 57. The detent pawl 58 fits in the opening 459 and is spring-pressed against the ratchet 56. y f

The end 62 of the shaft 57 receives the collar 60, which carries the gear 61. VThe outer end of the shaft 62 carries the floating. thrust collar. The gear 61`1neshes with the gear 64' mounted upon the. shaft 65 bythe collar 66.

67 on the top of the cover A. The housing `67 is closed by a cover 68,' held by bolts extending through the opening 69.. Between the cover 68 and the housing 67 is the gasket 72 for making an oil-tight connection.

NThe 'detent-pawl 58, as shown in Fig. 2, has a return spring 70 which is stressed4 by the screw plug 71 projecting in the side of the housing 67.

The pin 73 (see Fig. 2) projects into the recess left by the tlat'or'groove74 in the detent 58 and limits rotary movement of the detent 58.

The shaft 65, which is driven by the gear 64 (see Fig. 4)- extends through the upper arm 95 (see Fig. 1) of the U-shaped bracket 114 attached to the cover A by the bolts 161 with the washers 162 (see Fig.'1). The shaft 65 is connected by the collar 96 to the worm 97. The lower end of' the shaft projects through the frame arm 98*y and below said arm 98 receives the washer 99 and collar 100.

The worm 97 (see Figs. l and 3) meshes with and drives the gear 101 on the shaft 102;y The. collar or washer 103 (seer Fig. 3) holds the gear V101 Vin position thereon. TheA shaft 102 also extends through the hub 104 carrying the recessed disk 105. The gear 101 is fixed' to the disk 105 to drive the same.

' Mounted on the'extension 106 of the hub 104 (see Fig.

3) is the cam 107 carrying the pin 108 (.see. Figs. 1 and gear 101A is positioned inside ofthe loose washer 144.

The cup 35 constitutes an enlarged outer extension of the sleeve 28 beyond the point 39 (see Fig. 4). The housing 27 for the shaft 29 has an enlarged mounting portion The shaft 102 (see Fig.`3,) extends into the opening 109 in the block 1'10 forming part of the bracket' B and is Y held in position by the set-Screw 111.

The arm 98 Vof the bracket B is slotted at 112 .(see Fig. 1) to permit passage of thefcarn'107. The block 110 is at the bottom of the vertical arm 113.

Depending from the block 114 (see Fig. 2), attached to the bracket B, is the pivot mounting 115 with the flattened side faces 116 yfor the double arm 117. The arms 117 are pivotally mounted by the bolt 118 (see Figs. 1 and 2) on saidrflattened element 115. Y

Between the arms 117 is positioned the roller or follower 119 which has a pivotv 120 `extending across the arms 117. The follower 119 rides on the cam 107. The arms 117 have the recessed portions 121 (see Fig. l) beyond which are the enlargements 122 and 123. The enlargements 122 ride between the elements 124.and 125 on the upper end of the piston 129. Y Y The pump body 127 ris mounted on the' arm 98 by the nut 126. T he pump body 127 has a cylinder `128 receiving the piston 129. The lower portion .of the cylinder is tapped', as'indicated atV 130, to receivevthe inlet check valve unit 131. v Y Y The lower 'end 132 of the body 127 receives a filter The gears `61 and 64 are received in a housing Vor box unit 133 having the mesh screens 134 and the strainer pad 135. The pad 135 is held in position by means of the clamp ring 136 and split ring 143.

The follower member 124 carries the cup 151 which receives the coil spring 152. The coil spring 152 at its upper end ts into a recess in the cover plate A (see also Fig. 12) and at its lower end presses the piston 129 downwardly.

The rod 145 (see Fig. 1) extends through the opening 146 in the cover A and through the sleeve 147. It terminates in the manual actuating pull button 148 above the cover A. The collars or disks 149 and 150 are posi` tioned on said rod 145 on opposite sides of said enlargements 123. The disk 149 serves as an up stop, but lits loosely on the reduced diameter portion 164 of the shaft 145 so that it cannot be employed to push downwardly on the arms 117. The disk 149 will be stopped in up-4 ward motion in recess 165.

The double lever 117 may be lifted manually, if desired, against the spring 152 by the knob 148. This will elevate the piston 129 to give an optional lubricant pressure application and also permit lling of the tubing lines after initial installation of the lubricating equipment.

The pivot mount element 115 (see Figs. 1 and 2) may be adjusted in height by the knurled adjustment member 155, which fits in the slot 163 in the block 114. The rod 157 (see Fig. 2) constituting an upward extension of the mounting 115 is threaded at 156 where it extends through a tapped opening in the knurled adjustment .wheel or member 155. The member 155 when turned will move pivot 118 upwardly or downwardly. The illister head 159 in the socket 160 limits the movement of rod 157 when making adjustment.

Raising the pivot mount element 115 will decrease the discharge volume of the pump, and lowering will increase the volume, within the limits permitted by upper and lower stops.

The outlet connections 175 and 176 from the cylinder 127 (see Figs. 1, 2 and 3) connect to the tubing 177 and 178 having the bend or bows 179 and 180 (see Fig. 3). The tubing is held in position by the compression bushings 181 and 182.

The tubing 177 is connected to the adaptor 183 (see Fig. 2) by the compression bushing coupling connections 184. The adaptor 183 is mounted in the cover A.

The tubing 178 is connected by the compression nut connection 185 to the ow meter unit 186 and has the same construction as the meter unit o-f Fig. 17.

'Ihe lubricant ow from the tubing 178 passes into the housing E. Any excess lubricant flows back into the passageway 187 (see Fig. l) and a depending drip pipe 188 extending down from the arm of the bracket B. The outlet connection from the tubing 177 is located at 189 on the cover A and it has a threaded periphery 190 (see Fig. 2) for connection to an external piping system.

In the embodiment of Figs. l to 4, the reciprocatory actuator lever 55 by the pawl 79 will drive the ratchet wheel 34 and the shaft 29.

The detent pawl 58 in cooperation with the ner toothed-ratchet wheel 56 will prevent retrograde movement upon reverse oscillation of the lever 55, there being about 30 teeth on the driver ratchet wheel 34 and about 60 teeth on the detent ratchet Wheel 56.

This reciprocatory movement of lever 55 will drive the shaft 65 through the meshing gearing 61 and 64. The shaft 65 will drive the worm 97, the gear 101 and the recessed disk 105.

The pin 108 of the cam 107 lits in the recess 137 in the disk 105. When the follower roller 119 passes over the peak 138 of the cam 107, the cam 107 will snap forwardly with the pin 108 moving toward the other side of the recess 137. f

As the notch 137 in the disk portion of 105 drives the cam 107 through the pin 108, the double lever 117 will Yslowly elevate the piston 129 against the spring 152.

When the follower roller 119 passes over the top or lobe 138 of the cam 107, the spring 152 will force down the piston 129. A charge of oil will be forcedrthrough the tubing 177 into the external piping system through the connection 190.

At the same time a small amount of lubricant will be forced through the tubing 178 and the flow metering unit 186 into the housing 67. From the housing 67, the excess lubricant will llow back through the overflow and vent hole bore 139 on the shelf 140 (see Fig. 4) into the passageway 187 and the pipe 188.

When it is desired manually to actuate the piston 129,

the hand button 148 may be lifted. The dish 150 will then elevate the levers 117 and piston 129 against the spring 152.

Release lwill then permit a shot of lubricant to pass into the outlet lines 177 and 178. The cap or cover 24 may be opened to replenish the reservoir R. To adjust the pivot point of the levers 117, the knurled wheel may be adjusted or turned to elevate or lower the screw 156.

In Fig. 14 is diagrammatically shown the cyclic lubricator of Figs. 1 to 4 with the position of the cam mechanism and lubricator piston indicated as they are immediately before discharge. The double lever 117 has been actuated by the cam 107 so as to elevate the piston 129 to its highest position. In this position the recessed disk 105 with the recess 107 has driven the pin 108 to the position shown.

During the cycle leading up to the position of Fig. 14, the cam 107 Will have been slowly rotated by the gearing 97, 101, 61 and 64, and the lever 55 by the ratchet 34. This will result in slow movement upwardly of the piston or plunger 129 with the drawing of a measured volume of oil into the pump cylinder 128 past the filter 135. During this operation the check valve 131 will be'opened while the check valve unit 176 will be closed.

After the top of the cam stroke, as shown in Fig. 14, the cam 107 will snap forwardly with the pin 108 moving toward the other side of the recess in the disk 105. The discharge from the cylinder will take place rapidly under the action of the spring 152.

The frequency of the cycle is determined by the speed of oscillation of the lever 55 and by the reduction ratios of the gearing combinations of the gears 61 and 64 in the housing 67 and the worm 97 and the gear 101, as Well as the number of teeth engaged or picked-up in the ratchet 34 and by the throw of the lever 55.

The lever 55 may be driven by an eccentric crank or reciprocating part of the machine and the drive arm working angle may be in any position, but the operation should be positive in both directions. The directions of the drive of the ratchet 34 is preferably counter-clockwise, looking at the outer end of the lubricating drive shaft 29. For example, the working angle of the drive arms 55 may be varied from 18 to 90.

Typical reduction ratios corresponding to this range of degrees may vary from 38.5 to 3240. Correspondingly, the discharge in cubic centimeters per hour for 10 drive strokes of the lever 55 per minute may vary from 0.3 to 23.4 cubic centimeters.

Referring to Fig. 15, there is shown an arrangement for rotary continuous drive, without a ratchet, with a spiral gear connection. The extension 235 of the shaft 29 is flattened at 236. In this unit the shaft 235 may be driven from any rotating shaft, either direct or by a belt, chain or gear drive of suitable ratio. The direction of the drive may be lefthand or righthand, with suitable worms and gears.

In Fig. 16 is shown the application of the reciprocatory drive to a power press unit P. A ratchet drive such as shown in Figs. 1 to 5 is preferably used with a power press.

The power press P has a brake 248, a pitman 249, a guard 250 and the clutch or brake holder 251. It will be noted thatV the lubricator and reservoir R is provided with atubular connection 238 to the junctiony tting 239 ofl the gauge 240- to give a ready indication of the lubricant pressure in the system. Thereservoi'r is provided withl a sight glass 241. The reciprocating4 leverl 55 has a jointed connection at. 242' to the rod" 243.v Therod 243 in turn is pivotally` connected at 245 to the crank shaft 246 of the power press P'. The main ywheel 2,47 will rotate at constant speed and advance the crank shaft 246 one revolution for each press operation.

The lubricant may be fedV from the pump to the various bearings in and about the power press to flow meter l units of the type shown in Figs. 17 and 17a.

In Fig. 17 is shown a typical flow meter unit 260 having a threaded inlet end 261 and a threaded outlet end 262 tok be screwed into a bearing or machine part.

The central bore through the unit consists of an accurately drilled` passage 263.

The accurately drawn restriction pin 264 closely its in the passage.

-The fittings of Figs.,17 and 17a are normally connected in parallel and no matter where they are positioned in respect to the pump of Figs. 1 to 16, whether remote or nearby and regardless of the restriction through the bearing crevice, they will emit lubricant at their predetermined ratings and will accurately proportion the lubricantv even with widely varying lubricant' viscosities and widely varying pump pressure. v

To prevent any particles of dirt or dust clogging the narrow annular passageway,` av strainer 265 is positioned in the inlet pocket 266` backed up by a gauze 'cup 267. On the other hand, to prevent syphoning fromV an upper bearing to a lower bearing, the check valve 268 to provided, having a seating face of paper, oil silk, vinyl resin or silicone rubber with the spring 269 pressing said valve against the valve seat 270. Y Y Y The retainer 271 for the spring 269 will have the open-v ings 272 for ilow of oil. The outlet end' 262 is connected to a bearing and a pipe thread 262 enables the unit to be screweddirectly into the bearing or machinestructure.

The inlet end 261', as shown, connects to tubing 276 by coupling nut 277, tapered sleeve 278 and sleeve abutment 279. v

The fitting of Fig. 17a (correspondingly,functioning parts being indicated by the same numerals primed) is designed to be screwed into a junction or other position where lubricant is supplied under pressure from the pump of Figs. 1 to 4. In the fitting of Fig.i17a the inlet sleeve i275' serves ask an abutment in the recess in the junction, whilethe seat 274 functions in thesame manner as seat 279 in Fig. 17. v

In the embodiment of Figs.V 5 and 6, corresponding functioningY parts are indicated by the same` letters and numerals primed as in Figs. l' to 4. The shaft 29 has a reduced diameter external portion `200 receiving the driver ratchet 34. The nipple 201 fits in therecess bearing 202 in the cap 203 forming the upper part of th floating lever 55. .The lever 55 receives the pawl 79. The dowel pin 199 locates the cover A' in respect to pump bracket.

The shaft 29 turns -in the housing 27 and has a central bore 204 with transverse bores 205 for lubricant fed into the space 206 at the reducedv diameter portion 30 of the shaft 29.- The excess lubricant will ow through the recess 207 and the inclined bore 208 back to the reservoir.

The head 203 of the depending lever 55 has a sleeve extension 209 fitting inside of the collarv 43 and the enlarged head -40. ofthe housing 27. Y

ln` the lembodiment of Figs. 7, 8 and 9 correspondingly functioning parts are indicated by the samel letters and numerals as in Figs. 1 to 6, however provided with a superior 2.l v

Asv shown in Figs. 7 and 9, the detent 582yhas the flange 210 which is held in position by the bolt 21-1 tting'.v in the' tapped opening 212 of the cover A2. The

detent 582 has ya downwardly extending 1ip213- which.4

pini217` has the eccentric recess 218 which serves toi wedge the roller 21,4 against shaft section 219, giving a friction ratchet action. The detent 58,2 keeps theroller 214 from coming out.

In the embodiment of Figs. 10, ll, 12 and 13, corresponding functioning parts as thoseV shown in Figs. 1 to 9 are indicated by the same letters and numerals, how-v ever providedwith a superiorV 3. f n

The spring 1523 ts into the recess 225 in the cover A3 at its upper end. At its lower end the spring 1523 is received in cup 1513. The cup 1513 is attachedto the member 226 atV the upper end 1253 of the connectingY rod. The double arm 1173 has a pivot mountingv 1183. The adjustment for elevating or lowering the pivot 1183 consists of the rod 227 which fits in a bore 228 inthe block 229 of the bracketiB3. i

The follower 230 for the cam 1073 is held by the rivets 231 between the arms 1173. The gear 1013 drives thecam '1073 directly through the hub 1043'.

Referring to Fig. 18, there is shown an alternative ratchet drive assembly andV similarly functioning parts are indicated by the same numerals and letters as in Figs.y

1 toil3, provided however with asuperi'or 4. The arm 554 is not integral with sleeve 274, but press tted and riveted together at shoulder 300. Figs. 19 and 20, re.

spec-tively, show the drive teeth with there being about half as many'teeth on the drive ratchet 344 as there are on the detent ratchet 564.

Figs. 21 and 22 show one type of drive for the pump of Figs. 1 to 4 which is driven from the rotating member 600 with a knee action 599.

The lever 55 is connected by the lock nut 601 and the stud 602 to the double head 60S- 604; The elements 603 andV 604 are relatively pivotable. The head 604 is connected by sleeve 605, the nut 606 and threaded adjustment 607 to the tubular driving link 60S.

The sleeve 609 is mounted on member 600 is connected to the threaded adjustment 610 and the lock nut 611.

Figs. 23 and 24 show another type of drive from a reciprocating element namely the vertically reciprocating ram 615 with a knee action at 616. The connecting rods'or tubes 617 and 618 have threadedends 619, 620, 621 and 622 carrying the lock nuts 623, 624, 625 and 626 which ends are screwed into the tubular members 5S, 628, 629 and 630. The threaded tubular members 628 and 629 are pivotally connected at 616 and the tubular member 630 connects to the head 633 whichis mounted on the ram 615 by the screw 634 and lock nut 635.

The embodiment of the invention shown and described herein is to be considered merely as illustrative, as the invention is susceptible to variation, modification and change within the spirit and scope of the appended claim.

The element 55 referred to in Figs. 21 to 24 is a lever which actuates the input ratchet.

The knee action referred to as occurring at 599, 613, 616 and 633 in addition to the pivotal connection of the elements 609 and 639 to the rotating elements 600 and 615 will assure a reciprocating swinging motion of the levers 55.

Threaded adjustments are located at 607, 610, 619, 620 and 621.

Having now particularly described and ascertained the nature of the invention, and in what manner the same is to be performed, what is claimed is:

An automatic continuous ratchet drive for a reciprocating plunger pump for acentralized lubricating system comprisingv a cover plate carrying the pump mechanism and having a tubular enclosure `having an inside end and an outsideend and a box-like enclosure at the inside. end

of said tubular enclosure, a horizontal shaft positioned pawl to drive said shaft and means at the inside end l provided with a detent pawl acting on said detent ratchet, an intermeshing gear drive in said box-like enclosure driven by said shaft, a driving. arrangement for said plunger pump driven from said meshing gear drive, a first driving arm for said driving ratchet having end ilength adjustment means, -and `a driving link angularly positioned in respect to the first arm and pivotally connected lto the opposite end of the'rst arm away from the end of the lirst arm connected to the driving ratchet and a length vadjustment at an end of said driving link.

i References Cited lin the tile of thisrvpetent UNITED 'STATES PATENTS McCanna May 17, White Nov. 27, Niegemann Aug. 2, Zerk May 30, Leppla Mar. 22, Bijur Jan. 31, Hunting 7.--- June 17, Broden Sept. 16, Kocher Apr. 7, Kocher Jan. 19, Thomas June 14,

FOREIGN PATENTS Great Britain Apr. 29, France Oct. ,14l France vMay ,16, 

